EP0840012B1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
EP0840012B1
EP0840012B1 EP97308013A EP97308013A EP0840012B1 EP 0840012 B1 EP0840012 B1 EP 0840012B1 EP 97308013 A EP97308013 A EP 97308013A EP 97308013 A EP97308013 A EP 97308013A EP 0840012 B1 EP0840012 B1 EP 0840012B1
Authority
EP
European Patent Office
Prior art keywords
scroll
wrap
groove
tip
scroll wrap
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97308013A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0840012A1 (en
Inventor
Alexander Lifson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP0840012A1 publication Critical patent/EP0840012A1/en
Application granted granted Critical
Publication of EP0840012B1 publication Critical patent/EP0840012B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • This invention relates to a structure for minimizing separating pressure in a scroll compressor by tapping an intermediate suction pressure to the tip of at least one of the scroll members.
  • Scroll compressors are becoming widely accepted in the HVAC and refrigeration industries. Scroll compressors are relatively inexpensive, and typically more efficient and less noisy than reciprocating compressor counterparts. Scroll compressor technology has advanced greatly over the past several years. However, scroll compressor design still presents challenges in achieving reliable operation over a broad range of suction and discharge conditions. One major challenge is the reduction of the separating force between the orbiting and fixed scroll members.
  • Figure 1 is a view of a known scroll compressor 20.
  • An orbiting scroll 22 is driven through a shaft 24 to move relative to a fixed scroll 26 and compress a fluid captured between orbiting scroll 22 and fixed scroll 26.
  • Fixed scroll 26 has a scroll wrap 28 and the orbiting scroll has a scroll wrap 27.
  • the two scroll wraps contact each other at several points along the flanks, as well as opposing baseplates, that defines compression chambers between fixed and orbiting scroll wraps.
  • Refrigerant captured between orbiting scroll 22 and fixed scroll 26 creates a separating force tending to move the two scroll members away from each other. It is desirable to maintain the two scroll members in contact with each other to minimize leakage and avoid instability.
  • a scroll compressor becomes instable, the orbiting scroll is not in equilibrium. Instead, it may pivot or overturn until it comes in contact with another mechanical element. This action, coupled with the orbital movement of the orbiting scroll results in a sort of wobbling motion with axial contact occurring along the edge of the part. This wobbling, or instability, results in leakage through the gaps opened by the separated tips, edge loading of the scroll surfaces, and angular misalignment of the scroll drive bearing. All of these could quickly lead to loss of performance and premature failure of the compressor.
  • a back pressure chamber 29 is created between two sealing elements 30 and 32 mounted in a crankcase 33 which is also fixed to the fixed scroll 26.
  • Back pressure chamber 29 receives fluid from a tap, such as tap 34.
  • An example of a scroll compressor featuring a back pressure chamber is US 4,600,369 while EP 0065261 teaches reducing leakage between the high and low pressure chambers by means of a sealing member.
  • back chamber force is limited in magnitude, because of space limitations on the back chamber area and maximum achievable back chamber pressure.
  • the force in back pressure chamber 29 must overcome the separating force and press orbiting scroll 22 upwardly against fixed scroll, as well as be high enough to avoid orbiting scroll instability. The problem becomes most pronounced for refrigeration applications, with a broad range of operating pressures. Thus, it would be most desirable to reduce the separating force to minimize the restrictions on the compressor operating range.
  • the separating force across a portion of the scroll is shown graphically in Figure 2.
  • the dotted line 28 shows the location over the tip portion of scroll wrap. As is known, a higher pressure is applied on one side of wrap 28 and a lower pressure exists on the opposed side. The separating force is created by the pressure multiplied by the area over which the pressure is applied.
  • the present invention is directed to reducing the component of separating force applied across the scroll wrap tip.
  • the transition can be estimated by assuming a straight slope between the high pressure to the low pressure across the width of the wrap. While this estimation may not always be accurate, it is generally a good approximation. In practice, however, there are some variations and the pressure gradient is not always a constant slope.
  • the problem to be solved by this invention will be explained by reference to the constant pressure slope shown in Figure 2. However, it should be understood that the slope may be a curve or other irregular shape. The problem to be solved would still exist.
  • a disclosed embodiment of this invention minimizes the separating force component created by pressure across the scroll wrap tips.
  • low pressure fluid is tapped to a location between the scroll wrap tip and the opposed scroll plate.
  • the scroll wrap sees only low pressure for the majority of its width.
  • the high to low pressure gradient only occurs over a relatively small portion of the wrap width.
  • the present invention is particularly beneficial in refrigeration applications, where separating force and overturning moments are high.
  • One embodiment for achieving this invention utilizes shallow recesses extending axially into the scroll wrap. The recesses extend to the low pressure side of the scroll wrap and tap low pressure fluid into the space created by recesses on tip of scroll wrap.
  • the high to low pressure gradient does not essentially begin until a location past the recess.
  • the present invention thus reduces the high to low pressure gradient to a smaller portion of the wraps.
  • the remainder portion of the scroll wrap is maintained at the low pressure.
  • This invention has particular beneficial application in the type of scroll wrap having a wide width, which occurs in scroll wraps of varying width.
  • the recesses are separated from each other. This feature minimizes the likelihood of leakage along the scroll wrap in a circumferential direction from the high pressure side to the low pressure side.
  • the depth of the recess is less than 200 microns. More preferably, the depth of the recesses is 20 microns or less.
  • the intermediate pressure fluid is tapped into grooves or series of grooves, formed on the scroll wrap tip.
  • a tap to the low pressure fluid communicates into the groove.
  • the scroll wrap tip will see a low pressure between the groove and extending outwardly toward the low pressure side of the scroll.
  • the high to the low pressure gradient will occur from the groove to the side discharge pressure of the wrap. Since the gradient occurs over a relatively small portion of the width, the total separating force component from that gradient is reduced.
  • the groove may be relatively shallow, and of the same or larger depth as the recesses discussed above. Pressure taps communicate with the low pressure side of the scroll wrap to cap fluid to the groove. Also the groove may be separated into multiple grooves each communicating with a pressure tap.
  • the taps are made in a form of a recess located on the scroll wrap tip.
  • the recess can be machined at an angle and connected to the groove at the location closest to the low pressure.
  • FIG. 3 shows a scroll wrap 41. While the scroll wrap 41 may represent either the orbiting or fixed scroll wrap, in a most preferred embodiment, at least the fixed scroll wrap is provided with the inventive structure, since often it is thicker than the orbiting scroll.
  • Shallow recesses 42 are formed on the tip of the fixed scroll wrap 41. The shallow recesses 42 extend to an inner wall 44, adjacent to the high pressure side 45 of the scroll wrap 41. Recesses 42 extend to the low pressure side 46 of the scroll wrap 41. Thus, low pressure fluid from side 46 moves into recesses 42 and to wall 44.
  • Separating walls 48 are formed between the recesses 42. The separating walls 48 define discrete recesses, which reduce leakage along the scroll wrap 41 in a circumferential direction.
  • the recess 42 extends from edge 46 to wall 44, and at a location spaced from side 45. Separating walls 48 extend intermediate adjacent recesses 42.
  • the recesses 42 in total extend along the circumferential length of the wrap. For ease of manufacturing, the same objective can be achieved with one single recess, however, additional leakage along the scroll wrap may occur.
  • the recesses 42 are shallow, and the depth as shown in Figure 4 is greatly exaggerated for illustration purposes.
  • the recess is preferably of a depth less than 200 microns, for a scroll wrap typically having an axial height of at least .5 inch and up to several inches. More preferably, the recess has a depth of 20 microns or less. The depth does not have to be uniform and can be tapering off towards the high pressure side.
  • Figure 5 is similar to figure 2 in that it graphically shows a component of the separating force across a portion of the scroll.
  • the high pressure extends to the outer end 45.
  • a low pressure 43 extends inwardly across the scroll wrap 41 to the wall 44. Between the wall 44 and the outer edge 45, the high pressure to low pressure gradient 47 occurs.
  • the separating force is reduced by minimizing the area over which high pressure is acted upon.
  • a line 49 shows where the gradient would have occurred with the prior art structure.
  • the area covered by the shaded portion below the gradient 47 and line 43 as occurs with this invention is proportional to the separating force component now occurring with the invented scroll wrap.
  • the area covered by the portion between gradient 47, line 43 and gradient 49 is proportional to the reduction in separating force achieved by this embodiment of the invention.
  • FIG. 6 A second embodiment is shown in Figure 6 having a scroll wrap 53.
  • Scroll wrap 53 is provided with a groove 50 formed of a number of groove components, at a location spaced toward the discharge pressure side 51 of the wrap 53.
  • the groove 50 extends along the length of wrap 53.
  • the groove 50 has a wall 52 spaced toward the high pressure side 51.
  • a tap 58 extends from the groove 50 outwardly to the low pressure side 54 of the wrap 53.
  • the groove 50 extends between wall 52 and an outer wall 55.
  • a further tap 56 extends into the wrap 53 and communicates with the tap 58.
  • the low pressure fluid is tapped into the grooves 50 through taps 58 and 56. Separating walls 59 are formed in the groove 50, again to minimize leakage.
  • the result is a plurality of discrete groove component portions each having individual taps 56 and 58.
  • the tap 58 extends outwardly to side 54 of the scroll wrap 49.
  • the groove is preferably angled toward the lower pressure areas, as shown.
  • the groove 50 is spaced toward the discharge pressure side 51 of the scroll wrap 53.
  • Figure 8 shows a small portion of a wrap 69 in a third embodiment 70 having groove portions 72 like those shown in the Figure 6 embodiment.
  • Taps 74 are formed in the face of the scroll tip and extend to the outer edge 75. These taps 74 may be angled as were the taps in the Figure 6 embodiment.
  • FIGs 3-6 are particularly valuable for thick scroll wraps. These are the types of scroll wraps as illustrated in the Figures 3-6 embodiments. For several reasons, varying width scroll wraps, which have relatively thick sections, have recently been utilized in many applications. In these types of scroll wraps, the separating force across the scroll wrap tips becomes a greater portion of the overall separating force. It is in those applications that this invention is particularly beneficial.
EP97308013A 1996-10-30 1997-10-10 Scroll compressor Expired - Lifetime EP0840012B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US739578 1996-10-30
US08/739,578 US5833443A (en) 1996-10-30 1996-10-30 Scroll compressor with reduced separating force between fixed and orbiting scroll members

Publications (2)

Publication Number Publication Date
EP0840012A1 EP0840012A1 (en) 1998-05-06
EP0840012B1 true EP0840012B1 (en) 2003-04-02

Family

ID=24972941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97308013A Expired - Lifetime EP0840012B1 (en) 1996-10-30 1997-10-10 Scroll compressor

Country Status (11)

Country Link
US (2) US5833443A (ja)
EP (1) EP0840012B1 (ja)
JP (1) JP2963886B2 (ja)
KR (1) KR100294175B1 (ja)
CN (1) CN1090718C (ja)
BR (1) BR9706217A (ja)
DE (1) DE69720368T2 (ja)
EG (1) EG20872A (ja)
ES (1) ES2191814T3 (ja)
MY (1) MY116998A (ja)
TW (1) TW368559B (ja)

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US6171086B1 (en) * 1997-11-03 2001-01-09 Carrier Corporation Scroll compressor with pressure equalization groove
US6015277A (en) * 1997-11-13 2000-01-18 Tecumseh Products Company Fabrication method for semiconductor substrate
US6146119A (en) * 1997-11-18 2000-11-14 Carrier Corporation Pressure actuated seal
US6196814B1 (en) * 1998-06-22 2001-03-06 Tecumseh Products Company Positive displacement pump rotatable in opposite directions
JP4153085B2 (ja) * 1998-06-23 2008-09-17 サンデン株式会社 スクロール型圧縮機
US6193487B1 (en) * 1998-10-13 2001-02-27 Mind Tech Corporation Scroll-type fluid displacement device for vacuum pump application
US6050792A (en) * 1999-01-11 2000-04-18 Air-Squared, Inc. Multi-stage scroll compressor
US6893234B2 (en) * 2003-01-16 2005-05-17 Scroll Technologies Non-circular centered seal for back pressure chamber
US6430959B1 (en) * 2002-02-11 2002-08-13 Scroll Technologies Economizer injection ports extending through scroll wrap
US6682329B1 (en) * 2003-01-03 2004-01-27 Scroll Technologies Cooling of hybrid scroll compressor wrap by suction pressure gas passages
US6709249B1 (en) * 2003-01-16 2004-03-23 Scroll Technologies Recess on tip of hybrid scroll compressor wrap to compensate for uneven thermal expansion
US10683865B2 (en) 2006-02-14 2020-06-16 Air Squared, Inc. Scroll type device incorporating spinning or co-rotating scrolls
JP2008267150A (ja) * 2007-04-16 2008-11-06 Sanden Corp 流体機械
GB2472637B (en) 2009-08-14 2015-11-25 Edwards Ltd Scroll Compressor With Plural Sealing Types
GB0914230D0 (en) 2009-08-14 2009-09-30 Edwards Ltd Scroll pump
GB2472776B (en) * 2009-08-14 2015-12-02 Edwards Ltd Scroll pump with tip seal pockets
US11047389B2 (en) 2010-04-16 2021-06-29 Air Squared, Inc. Multi-stage scroll vacuum pumps and related scroll devices
GB2489469B (en) 2011-03-29 2017-10-18 Edwards Ltd Scroll compressor
US20130232975A1 (en) 2011-08-09 2013-09-12 Robert W. Saffer Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle
JP6158056B2 (ja) * 2013-12-04 2017-07-05 株式会社日立産機システム スクロール式流体機械
KR101573598B1 (ko) * 2014-02-20 2015-12-01 엘지전자 주식회사 스크롤 압축기
KR101596583B1 (ko) * 2014-06-24 2016-02-22 엘지전자 주식회사 스크롤 압축기
US10508543B2 (en) 2015-05-07 2019-12-17 Air Squared, Inc. Scroll device having a pressure plate
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
EP3788262A4 (en) 2018-05-04 2022-01-26 Air Squared, Inc. LIQUID COOLING OF ORBITAL AND FIXED SCROLL COMPRESSOR, EXPANSION DEVICE OR VACUUM PUMP
US11067080B2 (en) 2018-07-17 2021-07-20 Air Squared, Inc. Low cost scroll compressor or vacuum pump
US20200025199A1 (en) 2018-07-17 2020-01-23 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
US11898557B2 (en) 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
US11885328B2 (en) 2021-07-19 2024-01-30 Air Squared, Inc. Scroll device with an integrated cooling loop

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Also Published As

Publication number Publication date
EP0840012A1 (en) 1998-05-06
CN1185540A (zh) 1998-06-24
BR9706217A (pt) 1999-09-14
DE69720368T2 (de) 2004-02-19
CN1090718C (zh) 2002-09-11
JPH10141254A (ja) 1998-05-26
MY116998A (en) 2004-04-30
KR100294175B1 (ko) 2002-01-15
DE69720368D1 (de) 2003-05-08
EG20872A (en) 2000-05-31
JP2963886B2 (ja) 1999-10-18
TW368559B (en) 1999-09-01
US5833443A (en) 1998-11-10
KR19980033289A (ko) 1998-07-25
US5873711A (en) 1999-02-23
ES2191814T3 (es) 2003-09-16

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